Humidity control device

ABSTRACT

A humidity controller apparatus comprises: a first heat exchange chamber ( 69 ) for accommodating a first heat exchanger ( 3 ), an adsorbent material being supported on a surface of said first heat exchanger ( 3 ); and a second heat exchange chamber ( 73 ), formed adjacently to said first heat exchange chamber ( 69 ), for accommodating a second heat exchanger ( 5 ), an adsorbent material being supported on a surface of said second heat exchanger ( 5 ). A first air inflow passage ( 63 ) and a first air outflow passage ( 65 ) are formed along one end surface in a thickness direction in which respective one surfaces of said two heat exchange chambers ( 69, 73 ) continue and which are arranged in a superimposed manner in the thickness direction of both said heat exchange chambers ( 69, 73 ). A second air inflow passage ( 57 ) and a second air outflow passage ( 59 ) are formed along another end surface which is an end surface where respective one surfaces of said two heat exchange chambers ( 69, 73 ) continue and which is situated face to face with said one end surface, and which are arranged in a superimposed manner in the thickness direction of both said heat exchange chambers ( 69, 73 ). Opening/closing means ( 35, . . . , 47 , . . . ) are provided for opening and closing openings ( 31   a   , . . . , 33   a , . . . ) for communication between said first heat exchange chamber ( 69 ) and said second heat exchange chamber ( 73 ), and each said inflow passage ( 57, 63 ) and each said outflow passage ( 59, 65 ).

TECHNICAL FIELD

The present invention generally relates to a humidity controllerapparatus and specifically to an air distribution mechanism.

BACKGROUND ART

Conventionally, humidity controller apparatuses for regulating thehumidity of air by making use of an adsorbent material have been knownin the prior art. One such humidity controller apparatus is disclosed inJapanese Patent Application Kokai Publication No. 1996-189667.

This humidity controller apparatus has an air passage through which astream of outdoor or room air flows and passes. And, a section of thepiping of a refrigerant circuit which performs a vapor compressionrefrigeration cycle by the circulation of refrigerant is disposed in theinside of the air passage. This piping section in the air passagefunctions as an evaporator or as a condenser. In addition, disposed onthe periphery of the piping in the air passage is a mesh member which isformed of a net-like member in which is encapsulated an adsorbentmaterial.

The adsorbent material of the mesh container is cooled by a flow ofrefrigerant traveling through the piping section, when the pipingsection functions as an evaporator. By the action of such cooling,moisture present in the room or outdoor air is adsorbed via the net-likemember. In addition, when the piping section functions as a condenser,moisture adsorbed onto the adsorbent material is desorbed when heated bythe refrigerant flowing through the piping section. As a result, theadsorbent material is regenerated.

PROBLEMS THAT INVENTION INTENDS TO SOLVE

However, in the above-described conventional humidity controllerapparatus, air distribution systems have not been considered at all, andsize reduction has been demanded. That is, it is necessary to switch theair distribution systems between the case where the piping sectionfunctions as an evaporator and the case where the piping sectionfunctions as a condenser. Especially, continuous adsorption andregeneration of the adsorbent material requires more complicated airsystems.

In the above-described conventional humidity controller apparatus,however, the piping as a means for cooling and heating air and the meshcontainer as a moisture-adsorbing means are formed and arrangedseparately. Therefore, the air flow systems become more complicated, andin addition, the size of the conventional humidity controller increases.

The present invention was conceived in view of the above problems. Anobject of the present invention is to improve the air systems for thepurpose of downsizing.

DISCLOSURE OF INVENTION

As illustrated in FIG. 1, a first invention is directed to a humiditycontroller apparatus, provided with an adsorbent material, forregulating the humidity of air by effecting moisture adsorption onto theadsorbent material and moisture desorption from the adsorbent material.In the humidity controller apparatus of the first invention, there isprovided a refrigerant circuit (1) which comprises a first heatexchanger (3) and a second heat exchanger (5); which performs a vaporcompression refrigeration cycle by the circulation of a refrigeranttheretbiough; and which alternately affects refrigerant condensation andevaporation in the first and second heat exchangers (3, 5). In addition,the adsorbent material, illustrated as element 14 in FIG. 2, issupported on at least a surface of the first heat exchanger (3).

In the first invention, the distribution of air of the first heatexchange chamber (69) and the second heat exchange chamber (73) isswitched by opening/closing control by means of the opening/closingmeans (35, . . . , 47, . . . ). As the result of this, moistureabsorption and moisture release are effected in the first and secondheat exchange chambers (69, 73).

The second invention provides a humidity controller apparatus accordingto the first invention, wherein four openings (33 a-33 d) which allowcommunication between the first heat exchange chamber (69) and thesecond heat exchange chamber (73) and the first air inflow passage (63)and the first air outflow passage (65) are positioned in close proximityto one another in a matrix direction. Four openings (31 a-31 d) whichallow communication between the first heat exchange chamber (69) and thesecond heat exchange chamber (73) and the second air inflow passage (57)and the second air outflow passage (59) are positioned in closeproximity to one another in a matrix direction. The eightopening/closing means (35, . . . , 47, . . . ) are each formed by adamper.

In the second invention, the direction in which air is distributed isswitched by opening/closing the eight dampers (35, . . . , 47, . . . ).As a result, moisture absorption and moisture release are realized inthe first heat exchange chamber (69) and the second heat exchangechamber (73).

The third invention provides a humidity controller apparatus accordingto the first invention, wherein the first air inflow passage (63) andthe first air outflow passage (65) are arranged symmetrically with thesecond air inflow passage (57) and the second air outflow passage (59).

In the third invention, the first air inflow passage (63), the first airoutflow passage (65), the second air inflow passage (57), and the secondair outflow passage (59) are placed in a compact arrangement, and theair distribution resistance is decreased.

The fourth invention provides a humidity controller apparatus accordingto the first invention, wherein the first heat exchanger (3) and thesecond heat exchanger (5) are provided in a refrigerant circuit (1)which performs a vapor compression refrigeration cycle by thecirculation of a refrigerant therethrough such that refrigerantcondensation and evaporation alternately occur in the first heatexchanger (3) and the second heat exchanger (5).

In the fourth invention, moisture absorption and regeneration of theadsorbent material are realized by refrigerant condensation andevaporation occurring in the first heat exchanger (3) and the secondheat exchanger (5).

The fifth invention provides a humidity controller apparatus accordingto the fourth invention, wherein dehumidifier means (80) for switchingrefrigerant circulation in the refrigerant circuit (1) and airdistribution is provided so that moisture in a stream of air flowingthrough a refrigerant evaporating heat exchanger (3, 5) is adsorbed bythe adsorbent material of the refrigerant evaporating heat exchanger (3,5) while the adsorbent material of a refrigerant condensing heatexchanger (5, 3) is regenerated by the release of moisture therefrom toa stream of air flowing through the refrigerant condensing heatexchanger (5, 3), whereby the stream of air dehumidified by theadsorbent material of the refrigerant evaporating heat exchanger (3, 5)is supplied to an indoor space.

In the fifth invention, the dehumidifier means (80) switches refrigerantcirculation in the refrigerant circuit (1) and air distribution, wherebyair dehumidification takes place in one heat exchanger (i.e., therefrigerant evaporating heat exchanger (3, 5)) and adsorbent-materialregeneration takes place in the other heat exchanger (i.e., therefrigerant condensing heat exchanger (5, 3)). As the result of this,dehumidification is carried out without interruption.

The sixth invention provides a humidity controller apparatus accordingto the fourth invention, wherein humidifier means (81) for switchingrefrigerant circulation in the refrigerant circuit (1) and airdistribution is provided so that moisture in a stream of air flowingthrough a refrigerant evaporating heat exchanger (3, 5) is adsorbed bythe adsorbent material of the refrigerant evaporating heat exchanger (3,5) while the adsorbent material of a refrigerant condensing heatexchanger (5, 3) is regenerated by the release of moisture therefrom toa stream of air flowing through the refrigerant condensing heatexchanger (5, 3), whereby the stream of air humidified by the adsorbentmaterial of the refrigerant evaporating heat exchanger (5, 3) issupplied to an indoor space.

In the sixth invention, humidifier means (81) switches refrigerantcirculation in the refrigerant circuit (1) and air distribution, wherebyair dehumidification takes place in one heat exchanger (i.e., therefrigerant evaporating heat exchanger (3, 5)) and air humidificationtakes place in the other heat exchanger (i.e., the refrigerantcondensing heat exchanger (5, 3)) and the adsorbent material thereof isregenerated. As the result of this, humidification is carried outwithout interruption.

The seventh invention provides a humidity controller apparatus accordingto the fourth invention, wherein dehumidifier means (80) for switchingrefrigerant circulation in the refrigerant circuit (1) and airdistribution is provided so that moisture in a stream of air flowingthrough a refrigerant evaporating heat exchanger (3, 5) is adsorbed bythe adsorbent material of the refrigerant evaporating heat exchanger (3,5) while the adsorbent material of a refrigerant condensing heatexchanger (5, 3) is regenerated by the release of moisture therefrom toa stream of air flowing through the refrigerant condensing heatexchanger (5, 3), whereby the stream of air dehumidified by theadsorbent material of the refrigerant evaporating heat exchanger (3, 5)is supplied to an indoor space. Humidifier means (81) for switchingrefrigerant circulation in the refrigerant circuit (1) and airdistribution is provided so that moisture in a stream of air flowingthrough a refrigerant evaporating heat exchanger (3, 5) is adsorbed bythe adsorbent material of the refrigerant evaporating heat exchanger (3,5) while the adsorbent material of a refrigerant condensing heatexchanger (5, 3) is regenerated by the release of moisture therefrom toa stream of air flowing through the refrigerant condensing heatexchanger (5, 3), whereby the stream of air humidified by the adsorbentmaterial of the refrigerant evaporating heat exchanger (5, 3) issupplied to an indoor space. The dehumidifier means (80) and thehumidifier means (81) are configured to operate switchably between adehumidification mode of operation and a humidification mode ofoperation.

In the seventh invention, the dehumidifier means (80) switchesrefrigerant circulation in the refrigerant circuit (1) and airdistribution, whereby air dehumidification takes place in one heatexchanger (i.e., the refrigerant evaporating heat exchanger (3, 5)) andadsorbent-material regeneration takes place in the other heat exchanger(i.e., the refrigerant condensing heat exchanger (5, 3)). As the resultof this, dehumidification is carried out without interruption. Inaddition, when switched to the humidifier means (81), refrigerantcirculation in the refrigerant circuit (1) and air distribution areswitched. Then, air dehumidification takes place in one heat exchanger(i.e., the heat exchanger (3, 5)) and air humidification takes place inthe other heat exchanger (i.e., the heat exchanger (5, 3)) and theadsorbent material thereof is regenerated. As the result of this,humidification is carried out without interruption.

EFFECTS OF INVENTION

Thus, in accordance with the first invention, it is arranged that: thefirst heat exchange chamber (69) and the second heat exchange chamber(73) are adjacently arranged; the inflow passages (57, 63) and theoutflow passages (59, 65) are arranged in a superimposed manner in thethickness direction of the first and second heat exchange chambers (69,73). This provides a downsized humidity controller apparatus. That is,air distribution systems are made simple in construction and thereduction of size is achieved.

Further, it is arranged that adsorbent materials are supported on thesurfaces of the first and second heat exchangers (3) and (5), therebyallowing integral formation of a heating/cooling means and anadsorption/desorption means. Such an arrangement makes it possible toprovide dehumidification and humidification with the omission of anadsorbent-material container. This results in a reduction in the numberof component parts, thereby making it possible to provide not only asimplified structure but also a downsized humidity controller apparatus.

Furthermore, it is arranged that adsorbent materials are supported onthe surfaces of the first and second heat exchangers (3) and (5). Suchan arrangement makes it possible to allow the refrigerant to directlycool or heat the adsorbent materials. As the result of this, theadsorption/desorption performance of the adsorbent materials is broughtto a maximum. This makes it possible to improve the efficiency ofadsorption/desorption and to provide a downsized humidity controllerapparatus.

In accordance with the second invention, the openings (31 a-31 d, 33a-33 d) are positioned in close proximity to one another in a matrixdirection and are opened/closed by the dampers (35, . . . , 47, . . . ),respectively. Accordingly, air distribution systems are made simple inconstruction and the reduction of size is achieved.

In accordance with the third invention, the first inflow and outflowpassages (63, 65) are arranged symmetrically with the second inflow andoutflow passages (57, 59). Therefore, the distribution resistance isreduced. As a result, it is possible to perform dehumidification andother like operation with high efficiency.

In accordance with the fourth invention, the vapor compressionrefrigeration cycle refrigerant circuit (1) is employed. Therefore, theadsorption and regeneration of adsorbent materials are carried out withhigh efficiency.

In accordance with the fifth or sixth invention, it is possible tocontinuously perform a dehumidification operation or a humidificationoperation with the omission of an adsorbent material container. Thisreduces the number of component parts, thereby making it possible toprovide not only a simplified structure but also a downsized humiditycontroller apparatus. Besides, a dehumidification operation or ahumidification operation are performed with high efficiency.

In accordance with the seventh invention, the operation is continued byswitching between dehumidification and humidification. This reduces thenumber of component parts, thereby making it possible to provide notonly a simplified structure but also a downsized humidity controllerapparatus. Besides, dehumidification or humidification is provided withhigh efficiency.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a circuit diagram showing a refrigerant circuit of a humiditycontroller apparatus according to an embodiment of the presentinvention;

FIG. 2 is a perspective view of a heat exchanger according to theembodiment of the present invention;

FIG. 3 is a plan view of a casing, with the omission of its top surfaceplate;

FIG. 4 is an end elevation view of the casing taken on line A-A of FIG.3;

FIG. 5 is an end elevation view of the casing taken on line B-B of FIG.3;

FIG. 6 is a side view of a damper when placed in the closed state;

FIG. 7 is a side view of the damper when placed in the open state;

FIG. 8 is a side view of a first modification of the damper when-placedin the closed state;

FIG. 9 is a side view of the first damper modification when placed inthe open state;

FIG. 10 is a side view of a second modification of the damper whenplaced in the closed state;

FIG. 11 is a side view of the second damper modification when placed inthe open state;

FIG. 12 is a plan view of the casing with the omission of its topsurface plate, illustrating a first operation during dehumidification;

FIG. 13 is a plan view of the casing with the omission of its topsurface plate, illustrating a second operation during dehumidification;

FIG. 14 is a plan view of the casing with the omission of its topsurface plate, illustrating a first operation during humidification;

FIG. 15 is a plan view of the casing with the omission of its topsurface plate, illustrating a second operation during humidification;

FIG. 16 is a psychrometric chart representing an air state of thehumidity controller apparatus of the present embodiment and that of aconventional humidity controller apparatus during dehumidificationoperation; and

FIG. 17 is a table showing respective data of the humidity controllerapparatus of the present embodiment and the conventional humiditycontroller apparatus during dehumidification operation.

BEST MODE FOR CARRYING OUT INVENTION

Hereinafter, an embodiment of the present invention will be described indetail with reference to the drawings.

As shown in FIGS. 1-5, a humidity controller apparatus of the presentembodiment effects room-air dehumidification and humidification, and hasa hollow, rectangular parallelepiped box-like casing (17). The casing(17) accommodates a refrigerant circuit (1) and other component parts.

Referring to FIG. 1, the refrigerant circuit (1) is a closed circuitformed by a sequential connection of a compressor (7), a four-wayswitching valve (9) which is a flow path switching means, a first heatexchanger (3) which is a first heat exchanger, an expansion valve (11)which is an expansion mechanism, and a second heat exchanger (5) whichis a second heat exchanger.

In addition, the refrigerant circuit (1) is charged with a refrigerant.The refrigerant circuit (1) is configured, such that a vapor compressionrefrigeration cycle is performed by the circulation of the refrigeranttherethrough.

One end of the first heat exchanger (3) is connected to the four-wayswitching valve (9). The other end of the first heat exchanger (3) isconnected to one end of the second heat exchanger (5) via the expansionvalve (11). The other end of the second heat exchanger (5) is connectedto the four-way switching valve (9).

With reference to FIG. 2, the first heat exchanger (3) and the secondheat exchanger (5) are each formed by a respective fin and tube heatexchanger of the cross fin type. More specifically, each of the firstand second heat exchangers (3) and (5) is provided with a large numberof aluminum fins (13) each shaped like a rectangular plate and copperheat transfer tubes (15) which penetrate the fins (13).

An adsorbent material is supported by means of dip forming (immersionforming) on the external surface of each fin (13) as well as on theexternal surface of each heat transfer tube (15).

As the adsorbent material, zeolite, silica gel, activated carbon,materials selected from the organic polymer family having hydrophilicproperties or water-absorbing properties, materials selected from theion-exchange resin family having carboxylic acid group or sulfonic acidgroup, and functional polymeric materials such as temperature-sensitivepolymers may be used.

In the present embodiment, the first heat exchanger (3) and the secondheat exchanger (5) are fin and tube heat exchangers of the cross fintype. Alternatively, different types of heat exchangers may be employed.For example, heat exchangers of the corrugated fin type may be used.

In addition, in the present embodiment, the adsorbent material issupported, by means of dip forming, on the external surface of each ofthe fins (13) and on the external surface of each of the heat transfertubes (15). Alternatively, the adsorbent material may be supported onthe external surfaces by any other techniques as long as its ability toprovide adsorption is not reduced.

The four-way switching valve (9) is so configured as to switch between afirst state that allows communication between the first and third portsand, at the same time, communication between the second and fourth ports(as indicated in FIG. 1(A)), and a second state that allowscommunication between the first and fourth ports and, at the same time,communication between the second and third ports (as indicated in FIG.1(B)). And, the four-way switching valve (9) is switched forestablishing a switch between a first operation in which the first heatexchanger (3) functions as a condenser while, simultaneously, the secondheat exchanger (5) functions as an evaporator and a second operation inwhich the second heat exchanger (5) functions as a condenser while,simultaneously, the first heat exchanger (3) functions as an evaporator.

Next, with reference to FIGS. 3-5, the inner structure of the casing(17) is described. Referring to FIG. 3, the casing (17) has a front side(which is shown as a lower side in the figure), a backside (upper side),a left-hand side (left side), and a right-hand side (right side). Inaddition, in FIGS. 4 and 5, the casing (17) has a top surface (which isshown as an upper side in the figure) and a bottom surface (lower side).

The casing (17) is square when viewed in plan and is shaped like a flatbox. The casing (17) has a left side plate (17 a) which is provided witha first suction opening (19) through which outdoor air OA is drawn inand a second suction opening (21) through which room air RA (return air)is drawn in. The casing (17) further has a right side plate (17 b) whichis provided with a first outlet opening (23) through which emission airEA is expelled outside the room and a second outlet opening (25) throughwhich humidity-conditioned air SA is supplied to an indoor space.

Disposed inside the casing (17) is a partition plate (27) which is apartition member. The partition plate (27) defines an air chamber (29 a)and an equipment chamber (29 b) inside the casing (17). The partitionplate (27) is disposed perpendicularly, i.e., in the direction of thethickness of the casing (17). Referring to FIGS. 4 and 5, the partitionplate (27) is disposed so as to extend from a top plate (17 e) of thecasing (17) (upper side) to a bottom plate (17 f) of the casing (17)(lower side). Furthermore, with reference to FIG. 3, the partition plate(27) is disposed so as to extend from a front plate (17 c) of the casing(17) (lower side) to a back plate (17 d) of the casing (17) (upperside). In addition, in FIG. 3, the partition plate (27) is positioned,such that it lies somewhat right relative to the central part of thecasing (17).

The equipment chamber (29 b) accommodates the compressor (7) and otherdevices in the refrigerant circuit (1) with the exclusion of the heatexchangers (3, 5). In addition, the equipment chamber (29 b) houses afirst fan (79) and a second fan (77). The first fan (79) is connected tothe first outlet opening (23) while, on the other hand, the second fan(77) is connected to the second outlet opening (25).

The air chamber (29 a) of the casing (17) is provided with a first-endsurface plate (33) which is a partition member, a second end surfaceplate (31) which is a partition member, and a central dividing plate(67) which is a partition member. The first end surface plate (33), thesecond end surface plate (31), and the dividing plate (67) are alldisposed perpendicularly, i.e., in the direction of the thickness of thecasing (17) and, as shown in FIGS. 4 and 5, these plates are disposed,such that they extend from the top surface plate (17 e) to the bottomsurface plate (17 e) in the casing (17).

As shown in FIG. 3, the first end surface plate (33) and the second endsurface plate (31) are disposed so as to extend to the partition plate(27) from the left side surface plate (17 a) in the casing (17). Inaddition, the first end surface plate (33) is positioned, such that itslightly overlies the central part of casing (17) in FIG. 3. On theother hand, the second end surface plate (31) is positioned, such thatit slightly underlies the central part of casing (17), as shown in FIG.3.

The dividing plate (67) is disposed so as to extend between the firstend surface plate (33) and the second end surface plate (31), as shownin FIG. 3.

And, in the casing (17), a first heat exchange chamber (69) isdivisionally formed as a compartment by the first end surface plate(33), the second end surface plate (31), the dividing plate (67), andthe partition plate (27). In addition, in the casing (17), a second heatexchange chamber (73) is divisionally formed as a compartment by thefirst end surface plate (33), the second end surface plate (31), thedividing plate (67), and the left side surface plate (17 a) of thecasing (17). In other words, the first heat exchange chamber (69) lieson the right-hand side in FIG. 3; the second heat exchange chamber (73)lies on the left-hand side in FIG. 3; and the first heat exchangechamber (69) and the second heat exchange chamber (73) are formedadjacently parallelly with each other.

The first heat exchanger (3) is disposed in the first heat exchangechamber (69) The second heat exchanger (5) is disposed in the secondheat exchange chamber (73).

A horizontal plate (61), serving as a partition member, is disposedbetween the first end surface plate (33) and the back plate (17 d) ofthe casing (17), such that it defines a first inflow passage (63) and afirst outflow passage (65). In addition, a horizontal plate (55),serving as a partition member, is disposed between the second endsurface plate (31) and the front plate (17 c) of the casing (17), suchthat it defines a second inflow passage (57) and a second outflowpassage (59).

The interior space of the casing (17) is divided vertically (i.e., inthe direction of the thickness of the casing (17)) into upper and lowerspaces by the horizontal plates (61, 55). And, in FIG. 4, the firstinflow passage (63) is formed on the top surface side while, on theother hand, the first outflow passage (65) is formed on the bottomsurface side. In FIG. 5, the second inflow passage (57) is formed on thetop surface side while, on the other hand, the second outflow passage(59) is formed on the bottom surface side.

That is, the first inflow passage (63) and the first outflow passage(65) are formed along one end surface in a thickness direction in whichrespective one surfaces of the first and second heat exchange chambers(69) and (73) continue, and are arranged in a superimposed manner in thethickness direction of the first and second heat exchange chambers (69,73).

In addition, a second air inflow passage (57) and a second air outflowpassage (59) which are formed along another end surface which is an endsurface where respective one surfaces of the heat exchange chambers (69,73) continue and which is situated face to face with the one endsurface, and which are arranged in a superimposed manner in thethickness direction of the heat exchange chambers (69, 73).

And, in FIG. 3, the first inflow passage (63) and the first outflowpassage (65) are arranged symmetrically with the second inflow passage(57) and the second outflow passage (59), in other words, they arearranged in plane symmetry on the basis of a central line that crossesthe first and second heat exchange chambers (69) and (73).

In addition, the first inflow passage (63) is in communication with thefirst suction opening (19). The first outflow passage (65) is incommunication with the first fan (79), thereby being in communicationwith the first outlet opening (23). The second inflow passage (57) is incommunication with the second suction opening (21). The second outflowpassage (59) is in communication with the second fan (77), thereby beingin communication with the second outlet opening (25).

As shown in FIG. 4, the first end surface plate (33) is provided withfirst to fourth openings (33 a, 33 b, 33 c, 33 d). The first to fourthopenings (33 a, 33 b, 33 c, 33 d) are provided with a first damper (47),a second damper (49), a third damper (51), and a fourth damper (53),respectively. These four openings (33 a-33 d) are positioned in closeproximity to one another in a matrix direction, in other words they arevertically laterally arranged in the form of squares in pairs. The firstopening (33 a) and the third opening (33 c) open to the first heatexchange chamber (69) while, on the other hand, the second opening (33b) and the fourth opening (33 d) open to the second heat exchangechamber (73).

The first opening (33 a) allows communication between the first inflowpassage (63) and the first heat exchange chamber (69). The third opening(33 c) allows communication between the first outflow passage (65) andthe first heat exchange chamber (69). In addition, the second opening(33 b) allows communication between the first inflow passage (63) andthe second heat exchange chamber (73). The fourth opening (33 d) allowscommunication between the first outflow passage (65) and the second heatexchange chamber (73).

As shown in FIG. 5, the second end surface plate (31) is provided withfifth to eighth openings (31 a, 31 b, 31 c, 31 d). The fifth to eighthopenings (31 a, 31 b, 31 c, 31 d) are provided with a fifth damper (35),a sixth damper (37), a seventh damper (39), and an eighth damper (41),respectively. The four openings (31 a, 31 b, 31 c, 31 d) are positionedin close proximity to one another in a matrix direction, in other wordsthey are vertically laterally arranged in the form of squares in pairs.The fifth opening (31 a) and the seventh opening (31 c) open to thefirst heat exchange chamber (69) while, on the other hand, the sixthopening (31 b) and the eighth opening (31 d) open to the second heatexchange chamber (73).

The fifth opening (31 a) allows communication between the second inflowpassage (57) and the first heat exchange chamber (69). The seventhopening (31 c) allows communication between the second outflow passage(59) and the first heat exchange chamber (69). In addition, the sixthopening (31 b) allows communication between the second inflow passage(57) and the second heat exchange chamber (73). The eighth opening (31d) allows communication between the second outflow passage (59) and thesecond heat exchange chamber (73).

The first to eighth dampers (47-53, 35-41) constitute opening andclosing means for opening and closing the openings (33 a-33 d, 31 a-31d). The description is made with a focus on the fifth to eighth dampers(35-41). The damper (35-41) has a vane part (43) shaped like a rectangleand a shaft part (45) arranged centrally in the vane part (43), as shownin FIGS. 6 and 7. The shaft part (45) supports the vane part (43) on thefirst end surface plate (33) or on the second end surface plate (31),such that the vane part (43) is rotatable. And, as shown in FIG. 7, thedamper (35-41) is configured so that the opening (31 a-31 d) is placedin the open state when the vane part (43) is placed in a horizontalposition. The other first to fourth dampers (47-53) are formed so as tohave the same structure as that of the fifth to eighth dampers (35-41).

The structure of the dampers (35-41) is not limited to the ones shown inFIGS. 6 and 7. That is, each damper (47-53, 35-41) may employ astructure shown in FIGS. 10 and 11 or a structure shown in FIGS. 8 and9.

Referring to FIGS. 8 and 9, there are shown fifth to eighth dampers(35-41) each of which is provided with two vane parts (43). Each damper(35-41) is configured, such that its two vane parts (43) rotateindividually upwards and downwards respectively, thereby placing theassociated opening (31 a-31 d) in the open state.

Referring to FIGS. 10 and 11, there are shown fifth to eighth dampers(35-41) each of which is provided with two vane parts (43). Each damper(35-41) is configured, such that its two vane parts (43) is foldedupwards, thereby placing the associated opening (31 a-31 d) in the openstate.

In addition, the present humidity controller apparatus is provided witha dehumidifier means (80) and a humidifier means (81). And, it isconfigured that the dehumidifier means (80) may be switched to functionas the humidifier means (81), and vice versa, thereby allowing a switchbetween a dehumidification mode of operation and a humidification modeof operation.

The dehumidifier means (80) switches the circulation of refrigerant inthe refrigerant circuit (1) and the distribution of air by the damper(47-53, 35-41) so that moisture present in a stream of air flowingthrough the first heat exchanger (3) or the second heat exchanger (5),whichever functions as a refrigerant evaporating heat exchanger, isadsorbed by adsorbent material while, on the other hand, adsorbentmaterial is regenerated by the release of moisture present in theadsorbent material to a stream of air flowing through the second heatexchanger (5) or the first heat exchanger (3), whichever functions as arefrigerant condensing heat exchanger, and the stream of air thusconverted into a stream of dehumidified air by the adsorbent material issupplied into the room.

On the other hand, the humidifier means (81) switches the circulation ofrefrigerant in the refrigerant circuit (1) and the distribution of airby the damper (47-53, 35-41) so that moisture present in a stream of airflowing through the first heat exchanger (3) or the second heatexchanger (5), whichever functions as a refrigerant evaporating heatexchanger, is adsorbed by adsorbent material while, on the other hand,adsorbent material is regenerated by the release of moisture present inthe adsorbent material to a stream of air flowing through the secondheat exchanger (5) or the first heat exchanger (3), whichever functionsas a refrigerant condensing heat exchanger, and the stream of air thusconverted into a stream of humidified air by the adsorbent material issupplied into the room.

Running Operation

Next, the running operation of the above-described humidity controllerapparatus is described. The humidity controller apparatus takes in astream of first air and a stream of second air and performs selectivelya dehumidification operation or a humidification operation. In addition,the humidity controller apparatus continuously performs dehumidificationand humidification operations by alternately repeating a first operationand a second operation. Besides, the humidity controller apparatusperforms dehumidification and humidification operations in fullventilation mode and, in addition, humidification and dehumidificationoperations in circulation mode.

Dehumidification Operation in Full Ventilation Mode

In a dehumidification operation during full ventilation mode by thedehumidifier means (80), outdoor air OA is brought in as the first airand is supplied to the room while, on the other hand, room air RA isbrought in as the second air and is discharged outside the room.

First Operation

In the first operation in which the first fan (79) and the second fan(77) are driven, the process of moisture adsorption in the second heatexchanger (5) and the process of adsorbent-material regeneration(moisture desorption) in the first heat exchanger (3) are carried out.In other words, in the first operation, moisture present in the outdoorair OA is adsorbed in the second heat exchanger (5) and moisturedesorbed out of the first heat exchanger (3) is given to the room airRA.

Referring to FIG. 1(A) and FIG. 12, during the first operation thesecond damper (49), the third damper (51), the eighth damper (41), andthe fifth damper (35) are placed in the open state while, on the otherhand, the first damper (47), the fourth damper (53), the sixth damper(37), and the seventh damper (39) are placed in the closed state. Thefirst heat exchanger (3) is supplied with a stream of room air RA. Thesecond heat exchanger (5) is supplied with a stream of outdoor air OA.

In addition, the four-way switching valve (9) changes state to a stateshown in FIG. 1(A). As a result, in the refrigerant circuit (1) thefirst heat exchanger (3) functions as a condenser and the second heatexchanger (5) functions as an evaporator.

That is, high-temperature, high-pressure refrigerant expelled out of thecompressor (7) flows into the first heat exchanger (3) as a heat carrierfor heating. In the first heat exchanger (3), the adsorbent materialssupported, respectively, on the external surface of each fin (13) and onthe external surface of each heat transfer tube (15) are heated. Thisheating causes moisture desorption from the adsorbent materials, wherebythe adsorbent materials are regenerated.

On the other hand, the refrigerant condensed in the first heat exchanger(3) is decompressed by the expansion valve (11). The post-decompressionrefrigerant flows into the second heat exchanger (5) as a heat carrierfor cooling. In the second heat exchanger (5), heat of adsorption isgenerated when the adsorbent material supported on the external surfaceof each fin (13) and the adsorbent material supported on the externalsurface of each heat transfer tube (15) adsorb moisture. The refrigerantin the second heat exchanger (5) absorbs the heat of adsorption and thenevaporates. The refrigerant evaporated is directed back to thecompressor (7) and repeats such a circulation.

In addition, an inflow of room air RA entering through the secondsuction opening (21) by drive of the first and second fans (79) and (77)travels through the second inflow passage (57) and flows to the firstheat exchange chamber (69) from the fifth opening (31 a). In the firstheat exchange chamber (69), moisture desorbed from the adsorbentmaterial of the first heat exchanger (3) is released to the room air RAand, in this way, the room air RA is humidified. The room air RA thushumidified becomes a stream of emission air EA. The emission air EAexiting the first heat exchange chamber (69) flows through the firstoutflow passage (65) by way of the third opening (33 c). Then, theemission air EA, after passing through the first fan (79), is dischargedoutdoors through the first outlet opening (23).

On the other hand, an inflow of outdoor air OA entering through thefirst suction opening (19) travels through the first inflow passage (63)and flows to the second heat exchange chamber (73) from the secondopening (33 b). In the second heat exchange chamber (73), moisture inthe outdoor air OA is adsorbed by the adsorbent material of the secondheat exchanger (5) and, in this way, the outdoor air OA is dehumidified.The outdoor air OA thus dehumidified becomes a stream of humidityconditioned air SA. The humidity conditioned air SA exiting the secondheat exchange chamber (73) flows through the second outflow passage (59)by way of the eighth opening (31 d). Then, the humidity conditioned airSA, after passing through the second fan (77), is supplied indoorsthrough the second outlet opening (25).

Upon completion of the execution of the first operation, the secondoperation is carried out.

Second Operation

In the second operation in which the first fan (79) and the second fan(77) are driven, the process of adsorption in the first heat exchanger(3) and the process of regeneration in the second heat exchanger (5) arecarried out. In other words, in the second operation, moisture presentin outdoor air OA is adsorbed in the first heat exchanger (3) andmoisture desorbed out of the second heat exchanger (5) is given to roomair RA.

Referring to FIG. 1(B) and FIG. 13, during the second operation thefirst damper (47), the fourth damper (53), the seventh damper (39), andthe sixth damper (37) are placed in the open state while, on the otherhand, the third damper (51), the second damper (49), the fifth damper(35), and the eighth damper (41) are placed in the closed state. And,the first heat exchanger (3) is supplied with a stream of outdoor airOA. The second heat exchanger (5) is supplied with a stream of room airRA.

In addition, the four-way switching valve (9) changes state to a stateshown in FIG. 1(B). As a result, in the refrigerant circuit (1) thesecond heat exchanger (5) functions as a condenser and the first heatexchanger (3) functions as an evaporator.

That is, high-temperature, high-pressure refrigerant expelled out of thecompressor (7) flows into the second heat exchanger (5) as a heatcarrier for heating. In the second heat exchanger (5), the adsorbentmaterials supported, respectively, on the external surface of each fin(13) and on the external surface of each heat transfer tube (15) areheated. This heating causes moisture desorption from the adsorbentmaterials, whereby the adsorbent materials are regenerated.

On the other hand, the refrigerant condensed in the second heatexchanger (5) is decompressed by the expansion valve (11). Thepost-decompression refrigerant flows into the first heat exchanger (3)as a heat carrier for cooling. In the first heat exchanger (3), heat ofadsorption is generated when the adsorbent material supported on theexternal surface of each fin (13) and the adsorbent material supportedon the external surface of each heat transfer tube (15) adsorb moisture.The refrigerant in the first heat exchanger (3) absorbs the heat ofadsorption and then evaporates. The refrigerant evaporated is directedback to the compressor (7) and repeats such a circulation.

In addition, an inflow of room air RA entering through the secondsuction opening (21) by drive of the first and second fans (79) and (77)travels through the second inflow passage (57) and flows to the secondheat exchange chamber (73) from the sixth opening (31 b). In the secondheat exchange chamber (73), moisture desorbed from the adsorbentmaterial of the second heat exchanger (5) is released to the room air RAand, in this way, the room air RA is humidified. The room air RA thushumidified becomes a stream of emission air EA. The emission air EAexiting the second heat exchange chamber (73) flows through the firstoutflow passage (65) by way of the fourth opening (33 d). Then, theemission air EA, after passing through the first fan (79), is dischargedoutdoors from the first outlet opening (23).

On the other hand, an inflow of outdoor air OA entering through thefirst suction opening (19) travels through the first inflow passage(63). The outdoor air OA flows into the first heat exchange chamber (69)from the first opening (33 a). In the first heat exchange chamber (69),moisture in the outdoor air OA is adsorbed by the adsorbent material ofthe first heat exchanger (3), whereby the outdoor air OA isdehumidified. The outdoor air OA thus dehumidified becomes a stream ofhumidity conditioned air SA. The humidity conditioned air SA exiting thefirst heat exchange chamber (69) flows through the second outflowpassage (59) by way of the seventh opening (31 c). Then, the humidityconditioned air SA, after passing through the second fan (77), issupplied indoors through the second outlet opening (25).

After execution of the second operation, the first operation is carriedout again. And, indoor space dehumidification is continuously carriedout by repetition of the first operation and the second operation.

Humidification Operation in Full Ventilation Mode

In a humidification operation in full ventilation mode by the humidifiermeans (81), room air RA is brought in as the first air and is dischargedoutside the room while, on the other hand, outdoor air OA is brought inas the second air and is supplied into the room.

First Operation

In the first operation in which the first fan (79) and the second fan(77) are driven, the process of adsorption in the second heat exchanger(5) and the process of regeneration in the first heat exchanger (3) arecarried out. In other words, in the first operation, moisture present inthe room air RA is adsorbed in the second heat exchanger (5) andmoisture desorbed out of the first heat exchanger (3) is given to theoutdoor air OA.

Referring to FIG. 1(A) and FIG. 14, during the first operation the firstdamper (47), the fourth damper (53), the seventh damper (39), and thesixth damper (37) are placed in the open state while, on the other hand,the third damper (51), the second damper (49), the fifth damper (35),and the eighth damper (41) are placed in the closed state. The firstheat exchanger (3) is supplied with a stream of outdoor air OA. Thesecond heat exchanger (5) is supplied with a stream of room air RA.

In addition, the four-way switching valve (9) changes state to a stateshown in FIG. 1(A). As a result, in the refrigerant circuit (1) thefirst heat exchanger (3) functions as a condenser and the second heatexchanger (5) functions as an evaporator.

That is, high-temperature, high-pressure refrigerant expelled out of thecompressor (7) flows into the first heat exchanger (3) as a heat carrierfor heating. In the first heat exchanger (3), the adsorbent materialssupported, respectively, on the external surface of each fin (13) and onthe external surface of each heat transfer tube (15) are heated. Thisheating causes moisture desorption from the adsorbent materials, wherebythe adsorbent materials are regenerated.

On the other hand, the refrigerant condensed in the first heat exchanger(3) is decompressed by the expansion valve (11). The post-decompressionrefrigerant flows into the second heat exchanger (5) as a heat carrierfor cooling. In the second heat exchanger (5), heat of adsorption isgenerated when the adsorbent material supported on the external surfaceof each fin (13) and the adsorbent material supported on the externalsurface of each heat transfer tube (15) adsorb moisture. The refrigerantin the second heat exchanger (5) absorbs the heat of adsorption and thenevaporates. The refrigerant evaporated is directed back to thecompressor (7) and repeats such a circulation.

In addition, an inflow of room air RA entering through the secondsuction opening (21) by drive of the first and second fans (79) and (77)travels through the second inflow passage (57) and flows into the secondheat exchange chamber (73) from the sixth opening (31 b). In the secondheat exchange chamber (73), moisture in the room air RA is adsorbed bythe adsorbent material of the second heat exchanger (5), whereby theroom air RA is dehumidified. The room air RA thus dehumidified becomes astream of emission air EA. The emission air EA exiting the second heatexchange chamber (73) flows through the first outflow passage (65) byway of the fourth opening (33 d). Then, the emission air EA, afterpassing through the first fan (79), is discharged outdoors through thefirst outlet opening (23).

On the other hand, an inflow of outdoor air OA entering through thefirst suction opening (19) travels through the first inflow passage (63)and flows to the first heat exchange chamber (69) from the first opening(33 a). In the first heat exchange chamber (69), moisture desorbed outof the adsorbent material of the first heat exchanger (3) is released tothe outdoor air OA, whereby the outdoor air OA is humidified. Theoutdoor air OA thus humidified becomes a stream of humidity conditionedair SA. The humidity conditioned air SA exiting the first heat exchangechamber (69) flows through the second outflow passage (59) by way of theseventh opening (31 c). Then, the humidity conditioned air SA, afterpassing through the second fan (77), is supplied indoors through thesecond outlet opening (25).

Upon completion of the execution of the first operation, the secondoperation carried out.

Second Operation

In the second operation in which the first fan (79) and the second fan(77) are driven, the process of adsorption in the first heat exchanger(3) and the process of regeneration in the second heat exchanger (5) arecarried out. In other words, in the second operation, moisture presentin room air RA is adsorbed in the first heat exchanger (3) and moisturedesorbed out of the second heat exchanger (5) is given to outdoor airOA.

Referring to FIG. 1(B) and FIG. 15, during the second operation thesecond damper (49), the third damper (51), the eighth damper (41), andthe fifth damper (35) are placed in the open state while, on the otherhand, the fourth damper (53), the first damper (47), the sixth damper(37), and the seventh damper (39) are placed in the closed state. Thefirst heat exchanger (3) is supplied with a stream of room air RA. Thesecond heat exchanger (5) is supplied with a stream of outdoor air OA.

In addition, the four-way switching valve (9) changes state to a stateshown in FIG. 1(B). As a result, in the refrigerant circuit (1) thesecond heat exchanger (5) functions as a condenser and the first heatexchanger (3) functions as an evaporator.

That is, high-temperature, high-pressure refrigerant expelled out of thecompressor (7) flows to the second heat exchanger (5) as a heat carrierfor heating. In the second heat exchanger (5), the adsorbent materialssupported, respectively, on the external surface of each fin (13) and onthe external surface of each heat transfer tube (15) are heated. Thisheating causes moisture desorption from the adsorbent materials, wherebythe adsorbent materials are regenerated.

On the other hand, the refrigerant condensed in the second heatexchanger (5) is decompressed by the expansion valve (11). Thepost-decompression refrigerant flows to the first heat exchanger (3) asa heat carrier for cooling. In the first heat exchanger (3), heat ofadsorption is generated when the adsorbent materials supported,respectively, on the external surface of each fin (13) and on theexternal surface of the heat transfer tube (15) adsorb moisture. Therefrigerant in the first heat exchanger (3) absorbs the heat ofadsorption and then evaporates. The refrigerant evaporated is directedback to the compressor (7) and repeats such a circulation.

In addition, an inflow of air RA entering through the second suctionopening (21) by drive of the first and second fans (79) and (77) travelsthrough the second inflow passage (57). Then, the room air RA flows tothe first heat exchange chamber (69) from the fifth opening (31 a). Inthe first heat exchange chamber (69), moisture in the room air RA isadsorbed by the adsorbent material of the first heat exchanger (3),whereby the room air RA is dehumidified. The room air RA thusdehumidified becomes a stream of emission air EA. The emission air EAexiting the first heat exchange chamber (69) flows through the firstoutflow passage (65) by way of the third opening (33 c). Then, afterpassage through the first fan (79), the emission air EA is dischargedoutdoors through the first outlet opening (23).

On the other hand, an inflow of outdoor air OA entering through thefirst suction opening (19) travels through the first inflow passage(63). Then, the outdoor air OA flows into the second heat exchangechamber (73) from the second opening (33 b). In the second heat exchangechamber (73), moisture desorbed from the adsorbent material of thesecond heat exchanger (5) is released to the outdoor air OA, whereby theoutdoor air OA is humidified. The outdoor air OA thus humidified becomesa stream of humidity conditioned air SA. The humidity conditioned air SAexiting the second heat exchange chamber (73) flows through the secondoutflow passage (59) by way of the eighth opening (31 d). Then, afterpassage through the second fan (77), the humidity conditioned air SA issupplied indoors through second outlet opening (25).

Upon completion of the execution of the second operation, the firstoperation is carried out again. And, indoor space humidification iscontinuously carried out by repetition of the first operation and thesecond operation.

Dehumidification Operation in Circulation Mode

During a dehumidification operation in circulation mode by thedehumidifier means (80), room air RA is brought in as the first air andis supplied indoors while, on the other hand, outdoor air OA is broughtin as the second air and is discharged outdoors. The circulation ofrefrigerant in the refrigerant circuit (1) is the same as that in fullventilation mode and the description thereof is omitted accordingly.

First Operation

In the first operation, the process of adsorption in the second heatexchanger (5) and the process of regeneration (desorption) in the firstheat exchanger (3) are carried out. In other words, in the firstoperation, moisture present in room air RA is adsorbed in the secondheat exchanger (5) and moisture desorbed out of the first heat exchanger(3) is given to outdoor air OA.

During the first operation, the first damper (47), the third damper(51), the sixth damper (37), and the eighth damper (41) are placed inthe open state while, on the other hand, the second damper (49), thefourth damper (53), the fifth damper (35), and the seventh damper (39)are placed in the closed state. The first heat exchanger (3) is providedwith a stream of outdoor air OA. The second heat exchanger (5) isprovided with a stream of room air RA.

An inflow of outdoor air OA entering through the first suction opening(19) travels through the first inflow passage (63). Then, the outdoorair OA flows into the first heat exchange chamber (69) from the firstopening (33 a). In the first heat exchange chamber (69), moisturedesorbed from the adsorbent material of the first heat exchanger (3) isreleased to the outdoor air OA, whereby the outdoor air OA ishumidified. The outdoor air OA thus humidified becomes a stream ofemission air EA. The emission air EA exiting the first heat exchangechamber (69) flows through the first outflow passage (65) by way of thethird opening (33 c). Then, after passage through the first fan (79),the emission air EA is discharged outdoors through the first outletopening (23).

On the other hand, an inflow of room air RA entering through the secondsuction opening (21) travels through the second inflow passage (57).Then, the room air RA flows into the second heat exchange chamber (73)from the sixth opening (31 b). In the second heat exchange chamber (73),moisture in the room air RA is adsorbed by the adsorbent material of thesecond heat exchanger (5), whereby the room air RA is dehumidified. Theroom air RA thus dehumidified becomes a stream of humidity conditionedair SA. The humidity conditioned air SA exiting the second heat exchangechamber (73) flows through the second outflow passage (59) by way of theeighth opening (31 d). Then, after passage through the second fan (77),the humidity conditioned air SA is supplied indoors through the secondoutlet opening (25).

Upon completion of the execution of the first operation, the secondoperation is carried out.

Second Operation

In the second operation, the process of adsorption in the first heatexchanger (3) and the process of regeneration in the second heatexchanger (5) are carried out. In other words, in the second operation,moisture present in room air RA is adsorbed in the first heat exchanger(3) and moisture desorbed out of the second heat exchanger (5) is givento outdoor air OA.

During the second operation, the second damper (49), the fourth damper(53), the fifth damper (35), and the seventh damper (39) are placed inthe open state while, on the other hand, the first damper (47), thethird damper (51), the sixth damper (37), and the eighth damper (41) areplaced in the closed state. The first heat exchanger (3) is providedwith a stream of room air RA. The second heat exchanger (5) is providedwith a stream of outdoor air OA.

An inflow of outdoor air OA entering through the first suction opening(19) travels through the first inflow passage (63). Then, the outdoorair OA flows into the second heat exchange chamber (73) from the secondopening (33 b). In the second heat exchange chamber (73), moisturedesorbed from the adsorbent material of the second heat exchanger (5) isreleased to the outdoor air OA, whereby the outdoor air OA ishumidified. The outdoor air OA thus humidified becomes a stream ofemission air EA. The emission air EA exiting the second heat exchangechamber (73) flows through the first outflow passage (65) by way of thefourth opening (33 d). Then, after passage through the first fan (79),the emission air EA is discharged outdoors through the first outletopening (23).

On the other hand, an inflow of room air RA entering through the secondsuction opening (21) travels through the second inflow passage (57).Then, the room air RA flows into the first heat exchange chamber (69)from the fifth opening (31 a). In the first heat exchange chamber (69),moisture in the room air RA is adsorbed by the adsorbent material of thefirst heat exchanger (3), whereby the room air RA is dehumidified. Theroom air RA thus dehumidified becomes a stream of humidity conditionedair SA. The humidity conditioned air SA exiting the first heat exchangechamber (69) flows through the second outflow passage (59) by way of theseventh opening (31 c). Then, after passage through the second fan (77),the humidity conditioned air SA is supplied indoors through the secondoutlet opening (25).

After execution of the second operation, the first operation is carriedout again. And, indoor space dehumidification is continuously carriedout by repetition of the first operation and the second operation.

Humidification Operation in Circulation Mode

In a humidification operation in circulation mode by the humidifiermeans (81), outdoor air OA is brought in as the first air and isdischarged outdoors while, on the other hand, room air RA is brought inas the second air and is supplied indoors. The circulation ofrefrigerant in the refrigerant circuit (1) is the same as that in fullventilation mode and the description thereof is omitted accordingly.

First Operation

In the first operation, the process of adsorption in the second heatexchanger (5) and the process of regeneration in the first heatexchanger (3) are carried out. In other words, in the first operation,moisture present in outdoor air OA is adsorbed in the second heatexchanger (5) and moisture desorbed out of the first heat exchanger (3)is given to room air RA.

During the first operation, the second damper (49), the fourth damper(53), the fifth damper (35), and the seventh damper (39) are placed inthe open state while, on the other hand, the first damper (47), thethird damper (51), the sixth damper (37), and the eighth damper (41) areplaced in the closed state. The first heat exchanger (3) is suppliedwith a stream of room air RA. The second heat exchanger (5) is suppliedwith a stream of outdoor air OA.

An inflow of room air RA entering through the second suction opening(21) travels through the second inflow passage (57). Then, the room airRA flows into the first heat exchange chamber (69) from the fifthopening (31 a). In the first heat exchange chamber (69), moisturedesorbed from the adsorbent material of the first heat exchanger (3) isreleased to the room air RA, whereby the room air RA is humidified. Theroom air RA thus humidified exits the first heat exchange chamber (69)and flows through the second outflow passage (59) by way of the seventhopening (31 c). Then, after passage through the second fan (77), theroom air RA is supplied indoors through the second outlet opening (25).

On the other hand, an inflow of outdoor air OA entering through thefirst suction opening (19) travels through the first inflow passage(63). Then, the outdoor air OA flows into the second heat exchangechamber (73) from the second opening (33 b). In the second heat exchangechamber (73), moisture in the outdoor air OA is adsorbed by theadsorbent material of the second heat exchanger (5), whereby the outdoorair OA is dehumidified. The outdoor air OA thus dehumidified becomes astream of emission air EA. The emission air EA exiting the second heatexchange chamber (73) flows through the first outflow passage (65) byway of the fourth opening (33 d). Then, after passage through the firstfan (79), the emission air EA is discharged outdoors through the firstoutlet opening (23).

Upon completion of the execution of the first operation, the secondoperation is carried out.

Second Operation

In the second operation, the process of adsorption in the first heatexchanger (3) and the process of regeneration in the second heatexchanger (5) are carried out. In other words, in the second operation,moisture present in outdoor air OA is adsorbed in the first heatexchanger (3) and moisture desorbed out of the second heat exchanger (5)is given to room air RA.

During the second operation, the first damper (47), the third damper(51), the sixth damper (37), and the eighth damper (41) are placed inthe open state while, on the other hand, the second damper (49), thefourth damper (53), the fifth damper (35), and the seventh damper (39)are placed in the closed state. The second heat exchanger (5) issupplied with a stream of room air RA. The first heat exchanger (3) isprovided with a stream of outdoor air OA.

An inflow of room air RA entering through the second suction opening(21) travels through the second inflow passage (57). Then, the room airRA flows into the second heat exchange chamber (73) from the sixthopening (31 b). In the second heat exchange chamber (73), moisturedesorbed from the adsorbent material of the second heat exchanger (5) isreleased to the room air RA, whereby the room air RA is humidified. Theroom air RA thus humidified becomes a stream of humidity conditioned airSA. The humidity conditioned air SA exiting the second heat exchangechamber (73) flows through the second outflow passage (59) by way of theeighth opening (31 d). Then, after passage through the second fan (77),the humidity conditioned air SA is supplied indoors through the secondoutlet opening (25).

On the other hand, an inflow of outdoor air OA entering through thefirst suction opening (19) travels through the first inflow passage(63). Then, the outdoor air OA flows into the first heat exchangechamber (69) from the first opening (33 a); In the first heat exchangechamber (69), moisture present in the outdoor air OA is adsorbed by theadsorbent material of the second heat exchanger (5), whereby the outdoorair OA is dehumidified. The outdoor air OA thus dehumidified becomes astream of emission air EA. The emission air EA exiting the first heatexchange chamber (69) flows through the first outflow passage (65) byway of the third opening (33 c). Then, after passage through the firstfan (79), the emission air EA is discharged outdoors through the firstoutlet opening (23).

Upon completion of the execution of the second operation, the firstoperation is carried out again. And, indoor space humidification iscontinuously carried out by repetition of the first operation and thesecond operation.

Performance Comparison

Referring to FIG. 16, there is shown a psychrometric chart forcomparison between the dehumidification operation of a humiditycontroller apparatus of the present embodiment and the dehumidificationoperation of a conventional humidity controller apparatus. Both thehumidity controller apparatus of the present embodiment and theconventional humidity controller apparatus are capable of dehumidifyinga volume of air (about 150 m³) per hour.

Referring to FIG. 17, there is shown a table for comparison between thedata of the dehumidification operation of a humidity controllerapparatus of the present embodiment and the data of the dehumidificationoperation of a conventional humidity controller apparatus. The datashown in the table include information about the inlet temperature ofoutdoor air OA and other pieces of information. In addition, the symbols“{circle around (1)}”-“{circle around (8)}” indicated in FIG. 17correspond to the symbols “{circle around (1)}”-“{circle around (8)}”indicated in FIG. 16, respectively.

As is clear from FIGS. 16 and 17, the amount of dehumidification of thehumidity controller apparatus according to the present embodiment isgreater than the amount of dehumidification of the conventional humiditycontroller apparatus. More specifically, the amount of dehumidificationof the humidity controller apparatus according to the present embodimentis twice the amount of dehumidification of the conventional humiditycontroller apparatus.

Effects of Embodiment 1

As described above, according to the present embodiment, it is arrangedthat adsorbent materials are supported on the external surface of eachheat transfer tube (15) as well as on the external surface of each fin(13) in the first and second heat exchangers (3) and (5), therebyallowing integral formation of a heating/cooling means and anadsorption/desorption means. Such an arrangement makes it possible tocontinuously provide dehumidification and humidification with theomission of an adsorbent-material container. This results in a reductionin the number of component parts, thereby making it possible to providenot only a simplified structure but also a downsized humidity controllerapparatus.

Furthermore, it is arranged that adsorbent materials are supported onthe external surface of each heat transfer tube (15) as well as on theexternal surface of each fin (13) in the first and second heatexchangers (3) and (5). Such an arrangement makes it possible to allowthe refrigerant to directly cool or heat the adsorbent materials. As theresult of this, the adsorption/desorption performance of the adsorbentmaterials is brought to a maximum. This makes it possible to improve theefficiency of adsorption/desorption and to provide a downsized humiditycontroller apparatus.

That is, the contact thermal resistance is large if the adsorbentmaterial is brought into contact with only the external surface of eachfin (13). Thus, the effects of cooling and heating cannot be expected.In the present embodiment, adsorbent materials are supported on theexternal surface of each heat transfer tube (15) and the externalsurface of each fin (13) in the first and second heat exchangers (3) and(5), whereby the effects of cooling and heating are sufficientlyachieved.

Furthermore, it is arranged that adsorbent materials are supported onthe external surface of the first heat exchanger (3) as well as on theexternal surface of second heat exchanger (5). Such arrangement makes itpossible to continuously perform dehumidification and humidification. Asthe result of this, it becomes possible to perform dehumidification andhumidification with high efficiency.

In addition, it is arranged that: the first heat exchange chamber (69)and the second heat exchange chamber (73) are adjacently arranged; theinflow passages (57, 63) and the outflow passages (59, 65) are arrangedin a superimposed manner in the thickness direction of the first andsecond heat exchange chambers (69, 73). Such an arrangement provides adownsized humidity controller apparatus.

Besides, the eight dampers (35, . . . , 47, . . . ) are provided,whereby the direction in which air is distributed is switched. Thismakes it possible to achieve a switch in the distribution direction ofair by a simplified structure.

Furthermore, the first inflow and outflow passages (63, 65) are arrangedsymmetrically with the second inflow and outflow passages (57, 59). As aresult of such arrangement, the distribution resistance is reduced. Thismakes it possible to perform dehumidification and other like operationwith high efficiency.

In addition, the openings (31 a-31 d, 33 a-33 d) are positioned in closeproximity to one another in a matrix direction and are opened/closed bythe dampers (35, . . . , 47, . . . ), respectively. Accordingly, airdistribution systems are made simple in construction and the reductionof size is achieved.

Furthermore, the vapor compression refrigeration cycle refrigerantcircuit (1) is employed, the adsorption and regeneration of adsorbentmaterials are carried out with high efficiency.

Other Embodiments of Invention

In the foregoing embodiment, in each of the first heat exchanger (3) andthe second heat exchanger (5), adsorbent materials are supported on theexternal surface of each fin (13) as well as on the external surface ofeach heat transfer tube (15). In the present invention, however, it maybe arranged that adsorbent materials are supported on at least eitherone of the external surface of the fin (13) and the external surface ofthe heat transfer tube (15).

In addition, in the foregoing embodiment, adsorbent materials aresupported on both the first heat exchanger (3) and the second heatexchanger (5); however, it may be arranged that adsorbent material issupported on one of the heat exchangers, i.e., only on the first heatexchanger (3). In this case, moisture adsorption and moisture desorption(adsorbent material regeneration) take place at intervals.

Although in the foregoing embodiment the vapor compression refrigerationcycle refrigerant circuit (1) is employed to cool or heat the adsorbentmaterials of the first heat exchanger (3) and the second heat exchanger(5), cold water and hot water may be used instead. Specifically, theadsorbent materials may be cooled or heated by introducing a passage ofcold or hot water in the first heat exchanger (3) and the second heatexchanger (5).

Furthermore, the present invention is not limited to the arrangement ofthe embodiment shown in plan view (see FIG. 3). That is, the orientationof arrangement is not limited to that of the embodiment.

In addition, in the above-described embodiment, the first fan (79) isconnected to the first outlet opening (23). Alternatively, the first fan(79) may be provided so as to communicate with the first suction opening(19). In addition, the second fan (77) is connected to the second outletopening (25). Alternatively, the second fan (77) may be provided so asto communicate with the second suction opening (21). In other words, thefirst fan (79) and the second fan (77) may be of the draw-through typeor the forced draft type.

INDUSTRIAL APPLICABILITY

As has been described above, the humidity controller apparatuses of thepresent invention are useful in dehumidifying or humidifying an indoorspace or the like and are particularly suited for a structure where anadsorbent material is supported on the surface of a heat exchanger.

1. A humidity controller apparatus, comprising: a first heat exchangechamber (69) for accommodating a first heat exchanger (3), an adsorbentmaterial being supported on a surface of said first heat exchanger (3);a second heat exchange chamber (73), formed adjacently to said firstheat exchange chamber (69), for accommodating a second heat exchanger(5), an adsorbent material being supported on a surface of said secondheat exchanger (5); a first air inflow passage (63) and a first airoutflow passage (65) which are formed along one end surface in athickness direction in which respective one surfaces of said two heatexchange chambers (69, 73) continue and which are arranged in asuperimposed manner in the thickness direction of both said heatexchange chambers (69, 73); a second air inflow passage (57) and asecond air outflow passage (59) which are formed along another endsurface which is an end surface where respective one surfaces of saidtwo heat exchange chambers (69, 73) continue and which is situated faceto face with said one end surface, and which are arranged in asuperimposed manner in the thickness direction of both said heatexchange chambers (69, 73); and opening/closing means (35, . . . , 47, .. . ) for opening and closing openings (31 a, . . . , 33 a, . . . ) forcommunication between said first heat exchange chamber (69) and saidsecond heat exchange chamber (73), and each said inflow passage (57, 63)and each said outflow passage (59, 65).
 2. The humidity controllerapparatus of claim 1, wherein: four openings (33 a-33 d) which allowcommunication between said first heat exchange chamber (69) and saidsecond heat exchange chamber (73) and said first air inflow passage (63)and said first air outflow passage (65) are positioned in closeproximity to one another in a matrix direction; four openings (31 a-31d) which allow communication between said first heat exchange chamber(69) and said second heat exchange chamber (73) and said second airinflow passage (57) and said second air outflow passage (59) arepositioned in close proximity to one another in a matrix direction; andsaid eight opening/closing means (35, . . . , 47, . . . ) are eachformed by a damper.
 3. The humidity controller apparatus of claim 1,wherein said first air inflow passage (63) and said first air outflowpassage (65) are arranged symmetrically with said second air inflowpassage (57) and said second air outflow passage (59).
 4. The humiditycontroller apparatus of claim 1, wherein said first heat exchanger (3)and said second heat exchanger (5) are provided in a refrigerant circuit(1) which performs a vapor compression refrigeration cycle by thecirculation of a refrigerant therethrough such that refrigerantcondensation and evaporation alternately occur in said first heatexchanger (3) and said second heat exchanger (5).
 5. The humiditycontroller apparatus of claim 4, wherein dehumidifier means (80) forswitching refrigerant circulation in said refrigerant circuit (1) andair distribution is provided so that moisture in a stream of air flowingthrough a refrigerant evaporating heat exchanger (3, 5) is adsorbed bythe adsorbent material of said refrigerant evaporating heat exchanger(3, 5) while the adsorbent material of a refrigerant condensing heatexchanger (5, 3) is regenerated by the release of moisture therefrom toa stream of air flowing through said refrigerant condensing heatexchanger (5, 3), whereby the stream of air dehumidified by theadsorbent material of said refrigerant evaporating heat exchanger (3, 5)is supplied to an indoor space.
 6. The humidity controller apparatus ofclaim 4, wherein humidifier means (81) for switching refrigerantcirculation in said refrigerant circuit (1) and air distribution isprovided so that moisture in a stream of air flowing through arefrigerant evaporating heat exchanger (3, 5) is adsorbed by theadsorbent material of said refrigerant evaporating heat exchanger (3, 5)while the adsorbent material of a refrigerant condensing heat exchanger(5, 3) is regenerated by the release of moisture therefrom to a streamof air flowing through said refrigerant condensing heat exchanger (5,3), whereby the stream of air humidified by the adsorbent material ofsaid refrigerant evaporating heat exchanger (5, 3) is supplied to anindoor space.
 7. The humidity controller apparatus of claim 4, wherein:dehumidifier means (80) for switching refrigerant circulation in saidrefrigerant circuit (1) and air distribution is provided so thatmoisture in a stream of air flowing through a refrigerant evaporatingheat exchanger (3, 5) is adsorbed by the adsorbent material of saidrefrigerant evaporating heat exchanger (3, 5) while the adsorbentmaterial of a refrigerant condensing heat exchanger (5, 3) isregenerated by the release of moisture therefrom to a stream of airflowing through said refrigerant condensing heat exchanger (5, 3),whereby the stream of air dehumidified by the adsorbent material of saidrefrigerant evaporating heat exchanger (3, 5) is supplied to an indoorspace; humidifier means (81) for switching refrigerant circulation insaid refrigerant circuit (1) and air distribution is provided so thatmoisture in a stream of air flowing through a refrigerant evaporatingheat exchanger (3, 5) is adsorbed by the adsorbent material of saidrefrigerant evaporating heat exchanger (3, 5) while the adsorbentmaterial of a refrigerant condensing heat exchanger (5, 3) isregenerated by the release of moisture therefrom to a stream of airflowing through said refrigerant condensing heat exchanger (5, 3),whereby the stream of air humidified by the adsorbent material of saidrefrigerant evaporating heat exchanger (5, 3) is supplied to an indoorspace; and said dehumidifier means (80) and said humidifier means (81)are configured to operate switchably between a dehumidification mode ofoperation and a humidification mode of operation.